WO2019058934A1

WO2019058934A1 - Brake device

Info

Publication number: WO2019058934A1
Application number: PCT/JP2018/032438
Authority: WO
Inventors: 大河原　義之
Original assignee: Ｋｙｂ株式会社
Priority date: 2017-09-21
Filing date: 2018-08-31
Publication date: 2019-03-28
Also published as: JP2019056435A

Abstract

This brake device (100) is provided with: a brake body (10); support pins (21, 22) supported in an axially movable manner by a support frame (20) and supporting the brake body (10); a pressing mechanism (35) which is provided to a first caliper arm (12), presses a first brake lining (3) against a brake disk (2), and moves the brake body (10) in the axial direction of the support pins (21, 22) to press a second brake lining (4) against the brake disk (2); and a gap adjustment mechanism (40) by which the brake body (10) having moved in the axial direction of the support pins (21, 22) at the time of braking is returned in the opposite direction by a set distance when the braking is released. The gap adjustment mechanism (40) is provided to the support frame (20) and is configured so that the movement thereof in the axial direction of the support pins (21, 22) is restricted, and the movement thereof in the radial direction is permitted.

Description

Brake device

The present invention relates to a brake device.

JP 08-226 467 A is a floating disk brake having a support frame attached to a bogie of a railway vehicle, and a brake main body slidably supported in the axial direction of the wheel with respect to the support frame via a support pin. An apparatus is disclosed. In this disk brake device, a pair of caliper arms of the brake main body is provided to straddle the wheel (brake disc), and a pressing mechanism is provided for advancing and retracting the brake lining only to one of the caliper arms.

In the brake device of JP08-226467A, one caliper arm provided with the pressing mechanism is provided with a gap adjusting device for automatically adjusting the gap between the brake lining and the brake disc at the time of releasing the brake, but the pressing mechanism is provided. The other caliper arm that is not provided is not provided with a clearance adjustment mechanism. Therefore, there is a possibility that the other brake lining and the brake disc may come into contact with each other when the brake device is not braked. Therefore, the inventors of the present invention propose to move the brake body with respect to the support frame to adjust the gap between the other brake lining and the brake disc.

However, in the floating type brake device, the brake main body tilts with respect to the support frame so as to follow the tilting of the running wheel. Therefore, when moving the brake body with respect to the support frame to adjust the gap between the other brake lining and the brake disc, it is necessary to consider the inclination of the brake body with respect to the support frame.

An object of the present invention is to provide a brake device capable of adjusting a gap between a brake lining and a brake disc even when the brake body is inclined with respect to a support frame.

According to an aspect of the present invention, the brake device has first and second caliper arms supporting first and second brake linings capable of applying a frictional force by being in sliding contact with the brake disc from both sides of the brake disc. A brake body, a support pin axially movably supported by a support frame attached to a vehicle body or a carriage and supporting the brake body, a first caliper arm provided to press the first brake lining against the brake disc and the brake A pressing mechanism which moves the main body in the axial direction of the support pin to press the second brake lining against the brake disc, and a gap which returns the brake main body moved in the axial direction of the support pin at the time of braking An adjusting mechanism, the gap adjusting mechanism is provided on the support frame, and the axial direction of the support pin Movement move in the radial direction while being restricted to is allowed.

FIG. 1 is a plan view of a brake device according to an embodiment of the present invention. FIG. 2 is a front view of the brake device. FIG. 3 is a cross-sectional view taken along the line III-III in FIG. 1 and showing the periphery of the first support pin. FIG. 4 is a view showing a state in which the brake body is inclined in one direction with respect to the support frame. FIG. 5 is a view showing a state where the brake main body is inclined in the other direction with respect to the support frame. FIG. 6A is a conceptual diagram for explaining the movement of the clearance adjustment mechanism when the brake main body is inclined with respect to the support frame. FIG. 6B is a conceptual diagram for explaining the movement of a modification of the gap adjusting mechanism when the brake body is inclined with respect to the support frame. FIG. 7 is an enlarged cross-sectional view showing the vicinity of the gap adjusting mechanism and shows a non-braking state. FIG. 8 is an enlarged cross-sectional view showing the vicinity of the gap adjusting mechanism, and shows a case where the brake main body moves by less than the reference movement amount to be in a braking state. FIG. 9 is an enlarged cross-sectional view showing the vicinity of the gap adjusting mechanism, and shows a state in which the brake main body has moved by the reference movement amount. FIG. 10 is an enlarged cross-sectional view showing the vicinity of the gap adjusting mechanism, and shows a case where the brake main body moves beyond the reference movement amount to be in the braking state. FIG. 11 is a cross-sectional view of a brake device according to a modification of the present invention, showing the periphery of a first support pin. FIG. 12 is a cross-sectional view of a brake device according to another modification of the present invention, showing the periphery of the first support pin.

Hereinafter, embodiments of the present invention will be described with reference to the attached drawings.

First, the entire configuration of a brake device 100 according to an embodiment of the present invention will be described with reference to FIGS. 1 to 3.

The brake device 100 is a floating pneumatic brake for a railway vehicle in which compressed air is used as a working fluid. Instead of compressed air, other working fluid such as working oil may be used.

The brake device 100 applies a frictional force to the brake disc 2 rotating with the wheel 1. Specifically, the brake device 100 applies frictional force to the brake disc 2 by the first and

second brake linings

3 and 4 capable of applying frictional force by sliding contact with the brake disc from both sides of the brake disc 2. The rotation of the wheel 1 is braked.

The brake disc 2 is formed on both sides of the wheel 1 and rotates integrally with the wheel 1. Instead of forming the brake disc 2 integrally with the wheel 1, a separate brake disc 2 that rotates with the wheel 1 may be provided.

The brake device 100 is mounted on a brake main body 10 having first and

second caliper arms

12 and 14 respectively supporting the first and

second brake linings

3 and 4 via a guide plate 5 and a carriage (not shown). The first and second support pins 21 and 22 (see FIG. 2) which are axially movably supported by the support frame 20 and support the brake body 10, and the guide plate 5 supported by the first brake lining 3 The brake main body 10 is provided with a pair of anchor pins 33 supported so as to be able to move forward and backward, and a pressing portion 35 as a pressing mechanism that presses the first and

second brake linings

3 and 4 against the brake disc 2 by the pressure of compressed air.

The brake body 10 is supported by the bogie via the support frame 20 when the brake device 100 is applied to a railway vehicle. When the brake device 100 is applied to a vehicle other than a railway vehicle, the brake body 10 is supported by a vehicle body (not shown).

As shown in FIG. 1, the brake body 10 is a yoke that connects the first caliper arm 12 and the second caliper arm 14 with the first caliper arm 12 and the second caliper arm 14 extending so as to straddle the brake disc 2. It has the part 13 and the 1st,

2nd bracket parts

15 and 16 for supporting the brake main body 10 on a trolley | bogie.

The basic configurations of the peripheral structure of the first support pin 21 and the peripheral structure of the second support pin 22 are the same. Therefore, the peripheral structure of the first support pin 21 will be specifically described below, and the description of the second support pin 22 will be omitted.

The first support pin 21 is inserted into the insertion hole 20 a of the support frame 20 as shown in FIG. 3. Both ends of the first support pin 21 are respectively connected to the first and

second bracket portions

15 and 16 of the brake body 10. The first support pin 21 is provided parallel to the rotation axis of the wheel 1 and supported by the support frame 20 so as to be movable in the axial direction. Thus, the brake body 10 is supported by the support frame 20 so that the first support pin 21 can move in the axial direction.

As shown in FIG. 1, the exposed portion of the first support pin 21 is covered by a rubber boot 25 and protected from dust and the like. In this way, the brake body 10 is slidably supported floating relative to the support frame 20 by the first support pins 21. The illustration of the boot 25 is omitted except for FIG.

The first and

second brake linings

3 and 4 have

back plate portions

3a and 4a fixed to the guide plate 5, and

friction members

3b and 4b abutting on the brake disc 2 at the time of braking. The

friction members

3b and 4b consist of a plurality of segments and are fixed to the surfaces of the

back plate portions

3a and 4a. The first and

second brake linings

3 and 4 brake the rotation of the wheel 1 by the frictional force generated by the contact between the

friction members

3 b and 4 b and the brake disc 2.

The first and

second brake linings

3 and 4 face the brake disc 2 at predetermined intervals set in advance, respectively, when the brakes are not braked (the state shown in FIG. 1). At the time of braking, the first and

second brake linings

3 and 4 move toward the brake disc 2 in response to the pressing force of the pressing portion 35, and are pressed in contact with the brake disc 2 in parallel.

The guide plate 5 has a dovetail groove 5a which is formed along the longitudinal direction and in which the back plate portion 3a of the first brake lining 3 is engaged. The guide plate 5 is supported by the brake main body 10 at both longitudinal ends by the pair of anchor pins 33. One anchor pin 33 rotatably supports one end (upper end in FIG. 2) of the guide plate 5 on the brake body 10, and the other anchor pin 33 engages the other end (lower end in FIG. 2) of the guide plate 5 Lock on 10

The first caliper arm 12 of the brake body 10 has a pair of adjusters 30 disposed at both ends in the longitudinal direction (vertical direction in FIG. 2) and a pressing portion 35 disposed between the pair of adjusters 30. Provided.

The adjuster 30 adjusts the relative position of the first brake lining 3 to the brake disc 2 at a constant time when the brake is not being braked. The adjusters 30 are respectively fastened to the upper and lower end portions of the brake body 10 by the anchor bolts 32.

As shown in FIG. 1, the adjuster 30 is provided so as to be able to move forward and backward with respect to the lining receiver 31 fixed to the brake body 10 by the anchor bolt 32 and the lining receiver 31 to support the first brake lining 3 on the brake body 10 Anchor pin 33, a return spring (not shown) that biases the first brake lining 3 in a direction to move away from the brake disc 2, and the gap between the first brake lining 3 and the brake disc 2 is adjusted to a constant And a first gap adjusting mechanism (not shown).

When the first brake lining 3 approaches the brake disc 2, the anchor pin 33 is pulled out from the lining receiver 31 by the guide plate 5 displaced together with the first brake lining 3 and axially displaced. The anchor pin 33 resists the brake disc 2 from moving the first brake lining 3 in the circumferential direction by the frictional force at the time of braking when the first brake lining 3 is in sliding contact with the brake disc 2, thereby the first brake lining Hold three. The return spring and the first gap adjusting mechanism are accommodated on the inner periphery of the anchor pin 33.

The return spring is a coil spring that is compressed and interposed on the inner circumference of the anchor pin 33. When the brake device 100 changes from the braking state to the non-braking state, the anchor pin 33 pushes back the first brake lining 3 via the guide plate 5 by the biasing force of the return spring, and the first brake lining 3 is predetermined from the brake disc 2 Separate by a distance of As a result, the distance between the first brake lining 3 and the brake disc 2 at the time of non-braking can be adjusted, and the heat dissipation of the brake disc 2 can be improved. The braking state is a state in which the first and

second brake linings

3 and 4 are pressed by the brake disc 2 by the pressing portion 35 described later. The non-braking state is a state in which the pressing force pressed against the brake disc 2 by the pressing portion 35 does not act on the first and

second brake linings

3 and 4.

The first gap adjustment mechanism adjusts the amount of return of the first brake lining 3 due to the biasing force of the return spring at the time of non-braking when it is constant. That is, the first gap adjusting mechanism keeps the distance between the first brake lining 3 and the brake disc 2 constant at all times during non-braking.

As long as the wear amount of the first brake lining 3 is small and the stroke amount of the anchor pin 33 at the time of braking is small, the anchor pin 33 returns to the original position before braking at the time of non-braking.

On the other hand, when the wear of the first brake lining 3 progresses and the movement amount of the anchor pin 33 at the time of braking becomes large, the first gap adjusting mechanism is not braking at the time of braking. Advance the position of by the amount of the worn thickness. As a result, the distance between the first brake lining 3 and the brake disc 2 at the time of non-braking can be kept constant at all times.

The pressing portion 35 presses the first brake lining 3 against the brake disc 2 by the pressure of compressed air and moves the brake main body 10 in the axial direction of the first support pin 21 by its reaction force to brake the second brake lining 4. The disc 2 is pressed.

The pressing portion 35 can have any configuration as long as it presses the first and

second brake linings

3 and 4 against the brake disc 2. Therefore, although the detailed description of the pressing portion 35 is omitted, for example, the pressing portion 35 deforms the diaphragm by adjusting the air pressure in the pressure chamber provided inside, and causes the piston to withdraw from the cylinder by the deformation of the diaphragm. . Thereby, the pressing portion 35 presses the first brake lining 3 toward the brake disc 2 rightward in FIG. 1 via the guide plate 5, and the reaction force moves the brake body 10 leftward in FIG. The second brake lining 4 is pulled toward the brake disc 2. In this manner, the brake disc 2 is held between the first and

second brake linings

3 and 4 so that the frictional force as the braking force is exerted.

In the following, as shown in FIG. 1, the moving direction of the brake body 10 at the time of braking of the brake device 100, in other words, the movement of the brake body 10 such that the second brake lining 4 approaches the brake disc 2 and is pressed. The direction is referred to as "pressing direction". In addition, the moving direction of the brake main body 10 in which the second brake lining 4 and the brake disc 2 are separated is referred to as "canceling direction".

As shown in FIG. 3, the brake device 100 is provided in a spherical bearing 26 provided in the insertion hole 20 a of the support frame 20 and slidably supporting the first support pin 21, and in the insertion hole 20 a of the support frame 20. A pair of

rubber bushes

27 and 28 provided on both sides in the axial direction of the spherical bearing 26 and slidably supporting the first support pin 21 and the brake main body 10 moved in the axial direction of the first support pin 21 during braking. And a second gap adjusting mechanism as a gap adjusting mechanism for returning a set distance in the opposite direction when releasing the brake.

The spherical bearing 26 includes an outer ring 26a and an inner ring 26b having bearing surfaces slidably fitted to each other. The outer ring 26a and the inner ring 26b engage in relative rotation.

The outer ring 26 a is fitted to the inner peripheral surface of the insertion hole 20 a of the support frame 20. The first support pin 21 is slidably inserted into the inner ring 26b. Thus, the spherical bearing 26 pivotally supports the brake main body 10 with respect to the support frame 20 and slides in the axial direction of the first support pin 21 (rotational axis direction of the wheel 1) with respect to the support frame 20 Support floating as possible.

The support frame 20 has an engagement groove 29b formed on the inner peripheral surface, which restricts the movement of the second gap adjusting mechanism 40 in the axial direction by engaging a ring body 49 of the second gap adjusting mechanism 40 described later. The support frame 20 has a support frame main body 24 attached to a vehicle body or a carriage, and a fixing ring 29 attached to the support frame main body 24 and having an engagement groove 29b formed on the inner periphery.

The support frame main body 24 has an annular fixing groove 20b on the outer periphery of the end. The fixing groove 20b is a groove used to fix the boot 25 (see FIG. 1) when the second gap adjusting mechanism 40 is not provided.

The fixing ring 29 is attached to axial ends of the first and second support pins 21 and 22 in the support frame main body 24. The fixing ring 29 includes a locking portion 29 a locked to the fixing groove 20 b of the support frame main body 24, an engagement groove 29 b, a boot groove 29 c for attaching the boot 25, and the fixing ring 29 to the support frame main body 24. And an outer peripheral groove 29d to which a retaining ring (not shown) to be fixed is attached.

By providing the fixing ring 29, the second gap adjusting mechanism 40 can be easily assembled to the brake device 100, and can be easily retrofitted to the existing brake device 100, and assembly compatibility can be ensured. Furthermore, maintenance and replacement of each component of the second gap adjustment mechanism 40 can be easily performed.

The fixing ring 29 also has a locking portion 29a that is locked to the fixing groove 20b that is normally used to attach the boot 25, and a boot groove 29c for attaching the boot 25. As a result, the second gap adjusting mechanism 40 can be attached using the fixing groove 20b of the existing brake device 100, and the boot 25 can be attached as usual.

The second gap adjusting mechanism 40 separates the second brake lining 4 close to the brake disk 2 at the time of braking by a set distance at the time of releasing the braking. The second gap adjusting mechanism 40 is provided on the inner periphery of the fixing ring 29 and exerts a reaction force against the movement of the clamp portion 40a capable of clamping the first support pin 21 and the brake main body 10 at the time of braking. It has a release spring 50 as a biasing member for biasing the clamp portion 40 a and a ring body 49 provided on the outer periphery of the first support pin 21 and in contact with the support frame 20.

The ring body 49 axially supports the release spring 50 with the clamp portion 40a. The ring body 49 abuts on the end of the support frame 20. The ring body 49 is pressed against the end of the support frame 20 when the second gap adjustment mechanism 40 is in operation. The internal configuration of the second gap adjusting mechanism 40 will be described in detail later with reference to FIG.

The second gap adjusting mechanism 40 is provided on the support frame 20, and restricts axial movement of the first support pin 21 and permits radial movement.

Specifically, the inner diameter of the bottom of the engaging groove 29 b of the fixing ring 29 is formed larger than the outer diameter of the ring body 49 of the second gap adjusting mechanism 40. Therefore, even if the brake main body 10 is inclined with respect to the support frame 20, the ring body 49 can be moved in the engagement groove 29b to maintain the engaged state.

More specifically, when the distance between the inner diameter of the bottom of the engagement groove 29b and the outer diameter of the ring body 49 of the second gap adjusting mechanism 40 is the maximum inclination angle θmax [deg] of the brake body 10 with respect to the support frame 20 The displacement amount of the ring body 49 is larger than the displacement amount. Therefore, even when the brake main body 10 is inclined with respect to the support frame 20 by the maximum inclination angle θmax, the ring body 49 can move in the engagement groove 29 b and maintain the engaged state.

The brake body 10 is inclined in the left-right direction (the rotation axis direction of the wheel 1) with respect to the support frame 20 so as to follow the tilting of the wheel 1 during traveling. The maximum inclination angle θmax of the brake body 10 with respect to the support frame 20 is, for example, ± 3 [deg].

On the other hand, the second gap adjusting mechanism 40 is floatingly supported so as to be movable in the radial direction with respect to the support frame 20. Therefore, as shown in FIGS. 4 and 5, even when the brake body 10 is inclined with respect to the support frame 20 by the angle θ [deg] in one direction or the other direction, the ring body 49 of the second gap adjusting mechanism 40 At least a portion is engaged with the engagement groove 29 b of the fixing ring 29. Therefore, even in this state, the movement of the second gap adjusting mechanism 40 in the axial direction is restricted, so the second brake lining 4 close to the brake disk 2 can be separated by a set distance at the time of braking release. Therefore, in the floating brake device 100, the contact between the second brake lining 4 supported by the second caliper arm 14 where the pressing portion 35 is not provided and the brake disc 2 can be prevented.

In the second gap adjusting mechanism 40, as shown in FIG. 6A, the ring body 49 is formed in a circular shape. Thereby, at least a part of the ring body 49 is engaged with the engagement groove 29b of the fixing ring 29 even when the brake body 10 is inclined in the left-right direction with respect to the support frame 20 (a state shown by a two-dot chain line) ). Alternatively, as shown in FIG. 6B, the ring body 49 may be formed in an elliptical shape. In this case, the ring body 49 is arranged to move in the direction of the short side of the oval when the brake body 10 inclines to the left and right with respect to the support frame 20. Therefore, even if the brake body 10 is inclined in the left-right direction with respect to the support frame 20, the vicinity of the end of the long side of the oval long side of the ring body 49 is engaged with the engagement groove 29b of the fixing ring 29 (2 State shown by dotted line). As described above, the ring body 49 may have a shape in which at least a part is engaged with the engagement groove 29 b when the brake body 10 is inclined to the left and right with respect to the support frame 20.

Next, each member of the second gap adjusting mechanism 40 will be described with reference to FIG.

The release spring 50 is a coil spring that biases the clamp portion 40 a that clamps the first support pin 21 in the release direction.

When the brake body 10 and the first support pin 21 move in the pressing direction at the time of braking, the release spring 50 generates a reaction force to the movement, and the brake body 10 and the first support pin 21 move through the clamp portion 40a. And is biased in the release direction. Thereby, the brake main body 10 and the first support pin 21 are moved in the releasing direction by the biasing force of the release spring 50 when not braking, and a predetermined gap is formed between the second brake lining 4 and the brake disc 2.

Further, the brake body 10 and the first support pin 21 are urged in the release direction by the release spring 50 even in the non-braking state. This prevents the brake main body 10 and the first support pin 21 from moving in the pressing direction due to vibration of the vehicle or the like at the time of non-braking.

The clamp portion 40 a includes a retainer 41 as a wedge member having a wedge surface 41 a forming a wedge space with the outer peripheral surface of the first support pin 21, a rolling element 42 accommodated in the wedge space, and a rolling element 42. A clamp spring 43 as a pressing member for pressing the retainer 41 so as to press the wedge surface 41 a from the axial direction of the first support pin 21, and between the retainer 41 and the first support pin 21 in the radial direction And a cylindrical inner member 44 having a through hole 45a opening in the surface.

The retainer 41 is a cylindrical member provided on the outer periphery of the inner member 44. The retainer 41 has a tapered wedge surface 41 a that is inclined with respect to the axial direction of the first support pin 21. The retainer 41 forms a wedge space between the outer circumferential surface of the first support pin 21 and the wedge space whose radial interval gradually narrows along the axial direction of the first support pin 21 by the wedge surface 41 a.

A shim ring 41 b for adjusting a clearance and a fixing ring 41 c for fixing the shim ring 41 b to the retainer 41 are provided between the retainer 41 and a flange portion 47 described later of the inner member 44. By changing the thickness of the shim ring 41 b, the force with which the retainer 41 presses the rolling element 42 against the first support pin 21 can be adjusted.

The rolling element 42 is formed in a cylindrical shape, and contacts both the outer peripheral surface of the first support pin 21 and the wedge surface 41 a through the through hole 45 a. The rolling element 42 is not limited to a cylindrical shape, and may be formed in a spherical shape. Moreover, although the single rolling element 42 is shown in figure in FIG. 7, the number of the rolling elements 42 is not restricted to this, You may be provided with two or more. By providing the plurality of rolling elements 42, the clamp portion 40a can stably support the first support pin 21.

The inner member 44 is formed as a cylindrical main body 45 in which the through hole 45 a is formed, and extends radially outward from the outer peripheral surface of the main body 45 as a receiving portion for supporting the clamp spring 43 with the retainer 41. Spring receiving portion 46, a flange portion 47 as a supporting portion which is formed to extend radially outward from one end of the main body portion 45 and supports the release spring 50 with respect to the ring body 49; It has C ring 48 as a control part attached towards the diameter direction outside on the peripheral face of body part 45 in the side opposite to flange part 47.

The spring receiving portion 46 is provided on the opposite side to the flange portion 47 with the through hole 45 a interposed therebetween. The clamp spring 43 is interposed between the spring receiving portion 46 and the retainer 41 in a compressed state, and biases the retainer 41 in the right direction in FIG. 7 so that the rolling element 42 is pressed against the wedge surface 41a. Thereby, the rolling element 42 is pushed toward the narrow portion (left side portion in FIG. 7) in the wedge space. Thus, the relative movement between the clamp portion 40a and the first support pin 21 is restricted by the wedge effect. The clamp part 40a clamps the first support pin 21 in this manner.

The spring receiving portion 46 has a spring receiving surface 46 a against which the clamp spring 43 abuts, and an abutting surface 46 b against which the ring body 49 abuts. The spring receiver 46 is pressed against the C ring 48 by the biasing force of the clamp spring 43. The spring receiver 46 has an axial position defined by the C ring 48.

As shown in FIG. 7, in the non-braking state of the brake device 100, the contact surface 46b of the spring receiving portion 46 abuts on the ring body 49. When the spring receiving portion 46 and the ring body 49 abut, further movement of the clamp portion 40a in the releasing direction is restricted.

Next, the operation of the brake device 100 will be described with reference to FIGS. 7 to 10.

In FIGS. 8 to 10, the first support pin 21 in the non-braking state is indicated by a broken line. Also, in the following, the axial distance between the flange portion 47 of the clamp portion 40a and the second bracket portion 16 of the brake body 10 will be referred to as a "relative distance" between the clamp portion 40a and the brake body 10. Further, as shown in FIG. 7, the relative distance in the state where the second brake lining 4 is not worn is set to “L0”.

When the railway vehicle travels, the wheel 1 is rotating at high speed. Here, when the brake device 100 is switched to the braking state by the operation of the driver or the like, the pressing portion 35 (see FIG. 1) is moved to the first brake lining 3 via the guide plate 5 by the compressed air supplied from the air pressure source. Is pressed toward the brake disc 2 provided on the wheel 1.

At this time, a reaction force that causes the pressing portion 35 to press the first brake lining 3 acts on the brake body 10. Thereby, as shown in FIG. 8, the brake main body 10 is attached with the release spring 50 together with the first support pin 21 and the clamp portion 40a by the reaction force of the pressing portion 35 while keeping the relative distance L0 with the clamp portion 40a. It moves in the pressing direction against the force. Therefore, the second brake lining 4 is drawn toward the brake disc 2, and the first and

second brake linings

3 and 4 abut from both sides of the brake disc 2 to generate a frictional force, and the rotation of the wheel 1 is braked. Ru. As a result, the railway vehicle will stop at a reduced speed.

When the braking of the wheel 1 by the brake device 100 is released by the operation of the driver or the like, the first brake lining 3 separates from being in contact with the brake disc 2 by the restoring force of the return spring provided inside the adjuster 30. Do. Further, the compressed air in the pressure chamber is discharged from the through hole (not shown), and the first brake lining 3 returns to the position before braking.

Thereby, the brake disc 2 and the first brake lining 3 face each other again at a constant interval by the action of the first gap adjusting mechanism.

On the other hand, when the compressed air in the pressure chamber is discharged, the brake body 10, the first support pin 21, and the clamp portion 40a receive the biasing force of the release spring 50 compressed at the time of braking as a restoring force, and release direction Move towards The brake main body 10, the first support pin 21, and the clamp portion 40a move in the release direction until the contact surface 46b of the spring receiving portion 46 abuts on the ring body 49, and the state before braking (FIG. 7) State).

As a result, the brake disc 2 and the second brake lining 4 face each other with a constant gap, separated from each other. Therefore, the contact between the second brake lining 4 and the brake disc 2 when the brake device 100 is released is prevented. Thus, the wear of the second brake lining 4 can be suppressed, and the life of the second brake lining 4 can be improved. In addition, the wheel 1 can be rotated without being affected by the brake device 100.

When the friction member 3b of the first brake lining 3 wears, the guide plate 5 advances toward the brake disc 2 by the amount of wear of the friction member 3b by the first gap adjusting mechanism. Thus, the gap between the first brake lining 3 and the brake disc 2 is kept constant.

On the other hand, since the second caliper arm 14 is not provided with the first gap adjusting mechanism, the friction member 4b of the second brake lining 4 is worn (hereinafter referred to simply as "the second brake lining 4 is worn"). Then, the gap between the second brake lining 4 and the brake disc 2 becomes large. For this reason, in order to bring the second brake lining 4 and the brake disc 2 into contact from the non-braking state to make the braking state, the moving amount of the brake main body 10 moving in the pressing direction becomes large.

Here, in the brake device 100, when the brake body 10 moves in the pressing direction by the predetermined reference movement amount S0 from the non-braking state (state shown in FIG. 7), the first support pin 21 and the clamp portion 40a are relative to each other. The clamp 40 a and the release spring 50 are configured such that the force to be moved is balanced with the force for clamping the first support pin 21 by the clamp 40 a (hereinafter referred to as “clamping force”).

Specifically, during braking, the force for relatively moving the first support pin 21 and the clamp portion 40a (hereinafter simply referred to as "force for relatively moving") acts on the brake body 10 from the pressing portion 35. And the biasing force of the release spring 50 which acts on the clamp portion 40a and changes in accordance with the amount of movement of the clamp portion 40a. That is, the relative movement force is a reaction force of the pressing portion 35 acting in the pressing direction with respect to the brake main body 10 and the first support pin 21, and an urging force of the release spring 50 acting in the releasing direction with respect to the clamp portion 40a. And by. Since the reaction force of the pressing portion 35 is determined according to the desired braking force, the relative movement force is mainly determined by the biasing force of the release spring 50.

The clamp force of the clamp portion 40 a is a frictional force generated between the rolling element 42 and the first support pin 21 with respect to the relative movement force. The clamping force is determined by the biasing force of the clamp spring 43, the shape of the wedge surface 41a, the shape of the rolling element 42, the coefficient of friction between the first support pin 21 and the rolling element 42, and the like. By setting these appropriately, a desired clamping force can be obtained. The clamping force of the clamping unit 40 a is constant regardless of the amount of movement of the brake body 10. In FIGS. 8 to 10, the clamping force and the relative moving force are schematically indicated by arrows.

Hereinafter, the operation of the second gap adjusting mechanism 40 will be specifically described.

As shown in FIG. 8, when the wear of the second brake lining 4 is small and the moving amount of the brake body 10 is a moving amount S1 smaller than the reference moving amount S0, the force for relatively moving in the braking state is the clamp portion 40a. The clamp portion 40a and the first support pin 21 do not move relative to each other. That is, at the time of braking, the brake main body 10, the first support pin 21, and the clamp portion 40a are integrally pressed while maintaining the relative distance L0 while maintaining the first support pin 21 clamped by the clamp portion 40a. Move in the direction.

As shown in FIG. 9, when the amount of movement of the brake main body 10 at the time of braking becomes the reference amount of movement S0, the force for relative movement by the biasing force of the release spring 50 and the reaction force of the pressing portion 35 is the clamping force of the clamp portion 40a. Balance with. Hereinafter, the biasing force of the release spring 50 when the brake body 10 moves by the reference movement amount S0 is referred to as "reference biasing force".

If the brake body 10 tries to move in the pressing direction by exceeding the reference movement amount S0, the release spring 50 is further compressed, so that the force for relative movement is between the rolling element 42 and the first support pin 21. It exceeds the generated frictional force (clamping force). As a result, the clamp of the clamp portion 40a is released, and the first support pin 21 and the brake body 10 move in the pressing direction while exceeding the reference movement amount S0, while the clamp portion 40a is further pressed in the pressing direction. It does not move. Thus, relative movement between the clamp portion 40a and the first support pin 21 and the brake body 10 is permitted.

As described above, in the brake device 100 according to the present embodiment, the force for causing the relative movement to exceed the frictional force (clamping force) between the rolling element 42 and the first support pin 21 allows the clamp portion 40 a and the first support to be A state in which the pin 21 moves relative to the pin 21 is a state in which the clamp of the first support pin 21 by the clamp unit 40 a is released.

As shown in FIG. 10, the first support pin 21 and the brake main body 10 move relative to the clamp portion 40a by a movement amount S2 such that the brake device 100 is in the braking state. At this time, the relative distance between the brake body 10 and the clamp portion 40a is L1 smaller than L0. When the braking of the brake device 100 is released, the reaction force acting on the brake main body 10 from the pressing portion 35 disappears. For this reason, the force for moving the brake body 10 and the first support pin 21 relative to the clamp portion 40a is eliminated, and the force for moving the relative movement is less than the clamping force. Therefore, the first support pin 21 is again in a clamped state where it does not move relative to the clamp portion 40a. Thereby, the brake main body 10, the first support pin 21, and the clamp portion 40a move integrally in the releasing direction by the reference biasing force of the release spring 50. Therefore, the brake disc 2 and the second brake lining 4 are separated from each other and face each other again with a fixed gap.

More specifically, referring to FIGS. 8 to 10, the clamp unit 40a does not move in the pressing direction when the clamp is released, and the brake body 10 and the first support pin 21 move the reference movement amount S0. Move in the pressing direction beyond. The clamp part 40a in which the clamp is released clamps the first support pin 21 again after the braking of the brake device 100 is released.

As shown in FIGS. 8 and 9, before the clamp release where the movement amount of the brake body 10 is less than or equal to the reference movement amount S0, the relative distance between the brake body 10 and the clamp portion 40a is L0. (1) The support pin 21 is clamped. On the other hand, as shown in FIG. 10, when the clamp portion 40a moves relative to the brake body 10 and the first support pin 21 and clamps the first support pin 21 again, the relative distance is L1 smaller than L0. The first support pin 21 is clamped in position. That is, the position at which the first support pin 21 is clamped is shifted by the relative movement distance T between the clamp portion 40 a and the brake main body 10 as compared to before the clamp is released. Therefore, when the brake main body 10 is returned in the releasing direction by the release spring 50, the position of the brake main body 10 after the release of the braking is shifted by the relative movement distance T in the pressing direction.

Here, as shown in FIG. 10, even if the brake body 10 moves in excess of the reference movement amount S0, the clamp portion 40a does not move in the pressing direction, so the return amount of the release spring 50 in the releasing direction Is constant at the reference movement amount S0. Therefore, when the brake body 10 moves beyond the reference movement amount S0 to brake the wheel 1 and the braking is released, the brake disc 2 and the second brake lining 4 return the return amount (reference movement amount S0). Face each other with a certain gap depending on As described above, the release spring 50 and the clamp portion 40 a can exhibit a gap adjusting function of adjusting the gap between the second brake lining 4 and the brake disc 2. As a result, even if the wear of the second brake lining 4 progresses, the gap between the second brake lining 4 and the brake disc 2 can be appropriately secured.

As the amount of movement of the brake body 10 at the time of braking increases, the amount of compression of the release spring 50 also increases accordingly, and the biasing force of the release spring 50 biasing the clamp portion 40a also increases. The biasing force of the release spring 50 is a resistance to the movement of the brake body 10 at the time of braking, so if it becomes excessive, the pressing force of the second brake lining 4 against the brake disc 2 decreases and the braking force becomes unstable. There is a fear.

On the other hand, in the brake device 100, when the amount of wear of the second brake lining 4 increases and the amount of movement of the brake body 10 at the time of braking exceeds the reference amount of movement S0, the clamp by the clamp portion 40a is released. Therefore, the biasing force of the release spring 50 does not exceed the reference biasing force. In other words, even if the amount of wear of the second brake lining 4 increases, the reaction force from the release spring 50 is suppressed below the reference biasing force, and an increase in resistance to the movement of the brake body 10 can be suppressed. As described above, even if the brake main body 10 moves in the pressing direction by exceeding the reference movement amount S0, the biasing force of the release spring 50 is suppressed to be equal to or lower than the reference biasing force, and the stability of the braking force is secured.

As described above, in the brake device 100, the biasing force of the release spring 50 does not exceed the reference biasing force even if the moving amount of the brake main body 10 in the pressing direction exceeds the reference moving amount S0. The release spring 50 biases the clamp portion 40a to separate the second brake lining 4 and the brake disc 2 when braking is not performed, and the clamp is released when the reference movement amount S0 is exceeded, and the reaction force of the release spring 50. Can be suppressed. That is, the resistance to the movement of the brake body 10 at the time of braking is suppressed, and the second brake lining 4 and the brake disc 2 can be separated by the biasing force of the release spring 50 at the time of non-braking.

The reference movement amount S0 is determined such that the stability of the braking force and the life of the second brake lining 4 become desired. Specifically, according to the reaction force of the release spring 50 and the movement amount of the brake body 10 (the wear amount of the second brake lining 4), the clamp force and the release determined based on the configuration of the clamp portion 40a The relationship with the relative movement force determined by the spring 50 is adjusted and determined in advance.

Hereinafter, the clamping force and the relative moving force will be described in detail by showing a specific example.

The set load of the clamp unit 40a is set to, for example, 1000N. Further, the biasing force of the clamp spring 43 is set to, for example, about 200 N or less. Thereby, the clamping force of the clamp part 40a, ie, the frictional force between the rolling element 42 and the 1st support pin 21, becomes about 800N.

The biasing force (set load) of the release spring 50 in the non-braking state is set to, for example, about 500N. The biasing force of the release spring 50 is set so as not to exceed 800 N in a state where the brake main body 10 is moved by a movement amount equal to or less than the reference movement amount S0 and the second brake lining 4 contacts the brake disc 2. For example, the biasing force of the release spring 50 is about 700 N when the second brake lining 4 comes into contact with the brake disc 2 to be in a braking state with no wear occurring in the second brake lining 4.

When the brake body 10 moves in the pressing direction by the reference movement amount S0, the release spring 50 is compressed by that amount, and the reference biasing force of 800 N that balances the clamping force is exerted.

When the brake body 10 moves beyond the reference movement amount S0, the release spring 50 is further compressed and exerts an urging force of about 1000 N which is slightly larger than 800 N. Therefore, with the clamping force of 800 N, the relative movement between the clamp portion 40 a and the first support pin 21 can not be restricted, and both move relative to each other, and the clamp is released.

When the clamp by the clamp 40a is released, the clamp 40a does not move further in the pressing direction, and the reaction force of the release spring 50 does not increase. That is, the biasing force of the release spring 50 does not greatly exceed 800N. Therefore, even if the amount of movement of the brake body 10 increases beyond the reference amount of movement S0 during braking, the reaction force against the movement of the brake body 10 is suppressed to about 800N. Therefore, the contact between the second brake lining 4 and the brake disc 2 at the time of non-braking is prevented while securing the stability of the braking force of the brake device 100.

In addition, the above specific example showed only an example about a clamping force and the force made to move relatively, and the structure of the brake device 100 is not restricted to the said specific example. In the brake device 100, the force for moving relative to the clamping force may be configured as in the above-described example, or may be configured otherwise.

According to the above embodiment, the following effects can be obtained.

The second gap adjustment mechanism 40 restricts the axial movement of the first support pin 21 and is capable of radial movement. Therefore, even in a state where the brake body 10 is inclined with respect to the support frame 20, the movement of the second gap adjusting mechanism 40 in the axial direction is restricted. Therefore, even when the brake main body 10 is inclined with respect to the support frame 20, the brake main body 10 moved in the axial direction of the first support pin 21 at the time of braking is returned by the set distance in the opposite direction at the time of releasing the braking. Therefore, it is possible to provide the brake device 100 capable of adjusting the gap between the second brake lining 4 and the brake disc 2 even when the brake body 10 is inclined with respect to the support frame 20.

Further, in the brake device 100, the reaction force of the release spring 50 accompanying the movement of the brake main body 10 at the time of braking is applied to the first support pin 21 via the clamp portion 40a. Thereby, when the braking of the brake device 100 is released, the brake main body 10 is moved in the direction in which the second brake lining 4 and the brake disc 2 are separated by the reaction force. Therefore, the contact between the second brake lining 4 and the brake disc 2 when the brake device 100 is not braking is prevented. Therefore, the wear of the second brake lining 4 at the time of non-braking is suppressed, and the life of the second brake lining 4 can be improved.

In addition, the amount of movement of the brake body 10 necessary for braking increases due to the wear of the second brake lining 4, and when the brake body 10 moves in the pressing direction beyond the reference movement amount S0, the first support pin 21 and the clamp portion 40a Of the first support pin 21 and the rolling element 42 of the clamp portion 40a. Since the clamp portion 40a moves relative to the first support pin 21 without moving in the pressing direction, the reaction force of the release spring 50 does not increase even if the brake body 10 moves beyond the reference moving amount S0. As a result, even if the amount of movement of the brake body 10 increases beyond the reference amount of movement S0 during braking, an increase in reaction force with respect to the movement of the brake body 10 is suppressed. Therefore, while ensuring the stability of the braking force of the brake device 100, the gap between the second brake lining 4 and the brake disc 2 at the time of non-braking is appropriately secured to prevent contact between the two, The life of the lining 4 can be improved.

Further, in the brake device 100, the relative movement force and the clamping force are set so that the first support pin 21 and the clamp portion 40a move relative to each other when the movement amount of the brake body 10 exceeds the reference movement amount S0. There is. Therefore, the clamp can be released without providing a release mechanism for releasing the clamp, and the space around the clamp portion 40a can be saved, and the brake device 100 can be miniaturized.

Hereinafter, the configuration, operation, and effects of the embodiment of the present invention will be collectively described.

The brake device 100 which applies a frictional force to the brake disc 2 which rotates with the wheel 1 has first and

second brake linings

3 and 4 which can apply frictional force by being in sliding contact with the brake disc 2 from both sides of the brake disc 2 The brake body 10 having the first and

second caliper arms

12 and 14 to support, and the first and second support pins that are axially movably supported by the support frame 20 attached to the carriage and support the brake body 10 21 and 22, and provided on the first caliper arm 12, the first brake lining 3 is pressed against the brake disc 2 and the brake main body 10 is moved in the axial direction of the first and second support pins 21 and 22 to make the second brake The pressing portion 35 pressing the lining 4 against the brake disc 2 and the first and second support pins 21 and 22 during braking A second gap adjusting mechanism 40 for returning the brake main body 10 moved in the opposite direction by a set distance in the opposite direction at the time of releasing the braking; the second gap adjusting mechanism 40 is provided on the support frame 20; Axial movement of the

pins

21 and 22 is restricted and radial movement is allowed.

In this configuration, the movement of the first and second support pins 21 and 22 in the axial direction is restricted and the second gap adjustment mechanism 40 can move in the radial direction. Therefore, even in a state where the brake body 10 is inclined with respect to the support frame 20, the movement of the second gap adjusting mechanism 40 in the axial direction is restricted. Therefore, even when the brake body 10 is inclined with respect to the support frame 20, the brake body 10 moved in the axial direction of the first and second support pins 21 and 22 at the time of braking is returned by the set distance in the opposite direction at the time of braking release. Be Therefore, it is possible to provide the brake device 100 capable of adjusting the gap between the second brake lining 4 and the brake disc 2 even when the brake body 10 is inclined with respect to the support frame 20.

Further, the second gap adjusting mechanism 40 has a ring body 49 provided on the outer periphery of the first and second support pins 21 and 22 and in contact with the support frame 20, and the support frame 20 supports the first and second supports. An engagement groove 29b is formed on the inner peripheral surface of the insertion hole 20a through which the

pins

21 and 22 are inserted, and the ring body 49 is engaged to restrict the axial movement of the second gap adjusting mechanism 40. The inner diameter of the bottom of the groove 29 b is formed larger than the outer diameter of the ring body 49.

In this configuration, the inner diameter of the bottom portion of the engagement groove 29b is formed larger than the outer diameter of the ring body 49, so the ring body 49 is engaged even when the brake body 10 is inclined with respect to the support frame 20. The groove 29b can be moved to maintain the engaged state.

Further, the distance between the inner diameter of the bottom of the engagement groove 29b and the outer diameter of the ring body 49 is larger than the displacement of the ring body 49 at the maximum inclination angle θmax with respect to the support frame 20 of the brake body 10. Ru.

In this configuration, even when the brake body 10 is inclined with respect to the support frame 20 by the maximum inclination angle θmax, the ring body 49 can be moved in the engagement groove 29b to maintain the engaged state.

Further, the support frame 20 has a support frame main body 24 attached to a vehicle body or a carriage, and a fixing ring 29 attached to the support frame main body 24 and having an engagement groove 29 b formed on an inner periphery thereof.

In addition, the fixing ring 29 is attached to axial end portions of the first and second support pins 21 and 22 in the support frame main body 24.

In these configurations, by providing the fixing ring 29, the second gap adjustment mechanism 40 can be easily attached to the brake device 100, and can be easily retrofitted to the existing brake device 100, ensuring attachment compatibility. it can. Furthermore, maintenance and replacement of each component of the second gap adjustment mechanism 40 can be easily performed.

Further, the support frame main body 24 has an annular fixed groove 20b on the outer periphery, and the fixed ring 29 has a locking portion 29a which is locked to the fixed groove 20b.

In this configuration, the locking ring 29 has a locking portion 29a that is locked to the locking groove 20b normally used to attach the boot 25. As a result, the second gap adjusting mechanism 40 can be attached using the fixing groove 20b of the existing brake device 100.

Further, the second gap adjusting mechanism 40 exerts a reaction force against the movement of the brake main body 10 at the time of braking, and the brake main body 10 by the clamp portion 40 a capable of clamping the first and second support pins 21 and 22. And the release spring 50 which biases the clamp part 40a so as to resist movement of the

In this configuration, the reaction force of the release spring 50 accompanying the movement of the brake body 10 at the time of braking is applied to the first and second support pins 21 and 22 through the clamp portions 40 a and 140. Thereby, when the braking of the brake device 100 is released, the brake main body 10 is moved in the direction in which the second brake lining 4 and the brake disc 2 are separated by the reaction force. Therefore, the contact between the second brake lining 4 and the brake disc 2 when the brake device 100 is released is prevented. Therefore, the life of the second brake lining 4 of the brake device 100 can be improved.

In the state where the amount of movement of the brake main body 10 in the pressing direction in which the second brake lining 4 approaches the brake disk 2 is smaller than the reference movement amount S0, the brake device 100 causes the first and The second support pins 21 and 22 are clamped, and the clamps of the first and second support pins 21 and 22 are released when the brake main body 10 moves in the pressing direction beyond the reference movement amount S0.

In this configuration, the amount of movement of the brake body 10 necessary for braking increases due to the wear of the second brake lining 4, and when the brake body 10 moves in the pressing direction beyond the reference movement amount S0, the brake body 10 and the first and The second support pins 21 and 22 move relative to the clamp portion 40a. Therefore, even if the brake main body 10 moves beyond the reference movement amount S0, the clamp portion 40a does not move in the pressing direction, and the reaction force of the release spring 50 does not increase. Therefore, even if the amount of movement of the brake body 10 increases beyond the reference amount of movement S0 at the time of braking, an increase in reaction force with respect to the movement of the brake body 10 is suppressed. Therefore, the life of the second brake lining 4 is improved by preventing the contact between the second brake lining 4 and the brake disc 2 at the time of non-braking while securing the stability of the braking force of the brake device 100, 200. Can.

Further, in the brake device 100, a wedge space in which the clamp portion 40a gradually narrows along the axial direction of the first and second support pins 21, 22 is an outer peripheral surface of the first and second support pins 21, 22. And a rolling element 42 accommodated in the wedge space, and a clamp spring 43 pressing the retainer 41 such that the rolling element 42 is axially pressed against the wedge surface 41a. And.

Further, the brake device 100 further includes a cylindrical inner member 44 having a clamp portion 40a provided between the retainer 41 and the first and second support pins 21 and 22 and having a through hole 45a opened to the inner and outer peripheral surfaces. The rolling element 42 contacts the outer peripheral surface of the first and second support pins 21 and 22 through the through hole 45 a, and the inner member 44 supports the clamp spring 43 with the retainer 41. And a flange portion 47 supporting the release spring 50 between the ring body 49 and the ring body 49.

In these configurations, the clamp spring 43 biases the retainer 41 such that the rolling element 42 is pressed against the wedge surface 41 a. Thereby, the rolling element 42 is pushed toward the narrow portion in the wedge space. Thus, the relative movement between the clamp 40a and the first and second support pins 21 and 22 is restricted by the wedge effect, and the clamp 40a clamps the first and second support pins 21 and 22.

As mentioned above, although the embodiment of the present invention was described, the above-mentioned embodiment showed only a part of application example of the present invention, and in the meaning of limiting the technical scope of the present invention to the concrete composition of the above-mentioned embodiment. Absent.

For example, in the above embodiment, the second gap adjusting mechanism 40 is provided to the first and second support pins 21 and 22, respectively. Instead of this, the second gap adjusting mechanism 40 may be provided on only one of the first and second support pins 21 and 22.

Further, in the above embodiment, the fixing ring 29 is integrally formed so as to have the locking portion 29a locked to the fixing groove 20b of the support frame 20 and the boot groove 29c for attaching the boot 25. ing. Instead of this, as in the modified example shown in FIG. 11, a U-shaped ring 29e formed in a U-shaped cross-sectional shape and having a boot groove 29c and an U-shaped cross-sectional shape similarly to the inner periphery The fixed ring 29 may be formed by combining the fixed cover 29f on which the engagement groove 29b is formed. The fixed cover 29f is formed in a C-shape and is tightened by a bolt 29g to be ring-shaped. In this case, since it is a combination of two members having a U-shaped cross-sectional shape, the formation of the fixing ring 29 is easy.

Further, in the above embodiment, the fixing ring 29 is attached to the support frame main body 24 to form the engagement groove 29 b. Instead of this, as in the other modified example shown in FIG. 12, the engagement groove 29 b may be formed in the support frame main body 24 without providing the fixing ring 29. In this case, space saving around the support frame 20 can be achieved, and the brake device 100 can be miniaturized.

The present application claims priority based on Japanese Patent Application No. 2017-181722 filed on September 21, 2017, to the Japanese Patent Office, and the entire contents of this application are incorporated herein by reference.

Claims

A brake device which holds and brakes a brake disk rotating with a wheel, comprising:
A brake main body having first and second caliper arms supporting first and second brake linings which apply frictional force by sliding contact with the brake disc from both sides of the brake disc;
A support pin axially movably supported by a support frame attached to a vehicle body or a carriage and supporting the brake body;
A pressing mechanism provided on the first caliper arm to press the first brake lining against the brake disc and move the brake body in the axial direction of the support pin to press the second brake lining against the brake disc; ,
A gap adjusting mechanism for returning the brake main body, which has been moved in the axial direction of the support pin at the time of braking, in the opposite direction by a set distance at the time of releasing the braking;
The gap adjusting mechanism is provided on the support frame, and restricts axial movement of the support pin and permits radial movement.
Brake equipment.
The brake device according to claim 1,
The gap adjusting mechanism has a ring body provided on the outer periphery of the support pin and in contact with the support frame,
The support frame has an engagement groove which is formed on an inner peripheral surface of an insertion hole through which the support pin is inserted and which engages the ring body to restrict movement of the gap adjusting mechanism in the axial direction.
The inner diameter of the bottom of the engagement groove is formed larger than the outer diameter of the ring body.
Brake equipment.
The brake device according to claim 2, wherein
The distance between the inner diameter of the bottom of the engagement groove and the outer diameter of the ring body is formed to be greater than or equal to the displacement of the ring body at the maximum inclination angle of the brake body with respect to the support frame.
Brake equipment.
The brake device according to claim 2, wherein
The support frame is
A support frame body attached to the vehicle body or the carriage;
A fixing member attached to the support frame main body and having the engagement groove formed on an inner periphery thereof;
Brake equipment.
The brake device according to claim 4,
The fixing member is attached to an axial end of the support pin in the support frame main body.
Brake equipment.
The brake device according to claim 4,
The support frame main body has an annular fixing groove on the outer periphery,
The fixing member has a locking portion locked to the fixing groove.
Brake equipment.
The brake device according to claim 2, wherein
The clearance adjustment mechanism
A clamp portion capable of clamping the support pin;
And a biasing member that exerts a reaction force on the movement of the brake body at the time of braking and biases the clamp portion to resist the movement of the brake body.
Brake equipment.
The brake device according to claim 7, wherein
The support pin is clamped by the clamp unit in a state where the amount of movement of the brake main body in the pressing direction in which the second brake lining approaches the brake disc is less than a predetermined reference amount of movement, the brake main body When moving in the pressing direction by exceeding the reference movement amount, the clamp by the clamp unit is released.
Brake equipment.
The brake device according to claim 7, wherein
The clamp unit is
A wedge member having a wedge surface that forms a wedge space between the support pin and the outer circumferential surface of the support pin, the wedge space gradually decreasing in distance along the axial direction of the support pin;
Rolling elements accommodated in the wedge space;
And a pressing member that presses the wedge member or the rolling element so that the rolling element is axially pressed against the wedge surface.
Brake equipment.
The brake device according to claim 9,
The clamp portion further includes a cylindrical inner member provided between the wedge member and the support pin and having a through hole opened to the inner and outer peripheral surfaces,
The rolling element contacts the outer peripheral surface of the support pin through the through hole,
The inner member is
A receiving portion for supporting the pressing member with the wedge member;
And a support for supporting the biasing member between the ring and the ring body.
Brake equipment.